WO2009030761A1 - Low-energy valve system for a pressurized gas engine - Google Patents

Low-energy valve system for a pressurized gas engine Download PDF

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Publication number
WO2009030761A1
WO2009030761A1 PCT/EP2008/061808 EP2008061808W WO2009030761A1 WO 2009030761 A1 WO2009030761 A1 WO 2009030761A1 EP 2008061808 W EP2008061808 W EP 2008061808W WO 2009030761 A1 WO2009030761 A1 WO 2009030761A1
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WO
WIPO (PCT)
Prior art keywords
valve
volume chamber
movable member
variable volume
elements
Prior art date
Application number
PCT/EP2008/061808
Other languages
French (fr)
Inventor
Dominique Rochier
Original Assignee
Exosun
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Exosun filed Critical Exosun
Priority to CA2698499A priority Critical patent/CA2698499A1/en
Priority to US12/676,573 priority patent/US20100186720A1/en
Priority to EP08803777A priority patent/EP2185845A1/en
Publication of WO2009030761A1 publication Critical patent/WO2009030761A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/14—Check valves with flexible valve members
    • F16K15/144—Check valves with flexible valve members the closure elements being fixed along all or a part of their periphery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L11/00—Valve arrangements in working piston or piston-rod
    • F01L11/02—Valve arrangements in working piston or piston-rod in piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
    • F01L3/205—Reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2270/00—Constructional features
    • F02G2270/90—Valves

Definitions

  • the invention relates to a system comprising an intake or exhaust valve for a gas engine under pressure.
  • a pressurized gas engine is an expansion motor where a maximum pressure prevails substantially continuously in an intake duct or motor supply.
  • a particular embodiment of such a pressurized gas engine is an Ericsson type hot gas engine.
  • US 2005/0257523 discloses an Ericsson type hot gas engine having an intake valve and an exhaust valve both having a circular shaped flat head mounted at the end of a substantially cylindrical rod. The opening and closing of the exhaust and of the intake by these valves is effected by using a camshaft associated with each of the valves, pressing on the end opposite to the flat head of the cylindrical rod. of each of the valves. The camshafts are set in motion from the rotational movement of the crankshaft of the Ericsson engine.
  • One of the aims of the invention is to provide an improved system comprising an improved valve for either the intake or the exhaust for a pressurized gas engine that consumes little energy when it is being used. by allowing an optimal circulation of the gas under pressure using the engine.
  • a system for a gas engine under pressure comprising: - a variable volume chamber; and a valve comprising a first stationary member for enabling the valve to be attached to the engine, a second movable member for conditionally closing a gas communication passage with the variable volume chamber, first deformable connecting means elastically linking the first and second elements together, the chamber further comprising means for implementing the second movable member of the valve.
  • the valve comprises one of the following features: the valve is monobloc; the valve forms a substantially flat blade before deformation; the valve is substantially circular in shape; the first and second elements are in the form of concentric rings; at rest, the first and second elements are substantially in the same plane; at rest, the first and second elements are in two different planes substantially parallel to each other; -
  • the valve comprises a third movable member adapted to close a second gas communication passage with the variable volume chamber and second resiliently deformable connecting means connecting the second and third elements together; the third element is substantially planar disc shape; the first and / or second elastically deformable connecting means comprise tabs; the tongues are of substantially spiral shape and uniformly distributed over a circumference of the valve; the implementation means are intended to implement the third movable member of the valve; the implementation means comprise an elastically deformable element mounted on a piston delimiting the variable volume chamber; the elastic deformable element is of the compression spring type.
  • a pressurized gas engine comprising at least one
  • FIG. 1 is a three-dimensional view of an intake valve according to one embodiment of the invention
  • Figure 2a is a sectional view along II-II of the valve of Figure 1 at rest
  • Figure 2b is a sectional view along II-II of the valve of Figure 1 in the open position
  • - Figures 3a to 3d are simplified schematic sectional views of a pressurized gas engine illustrating the steps of admission of the hot gas under pressure in the variable volume chamber according to the invention
  • FIG. 4 is a three-dimensional, half-sectional view of a cylinder of a gas engine under pressure illustrating an exhaust valve according to the invention
  • Figure 5 is a three-dimensional top view of the cylinder of Figure 4
  • Figure 6 is an exploded partial three-dimensional view illustrating an alternative embodiment of the intake valve and the exhaust valve, both according to the invention.
  • the valve (1) is here in the form of a thin blade and a shape of revolution about an axis (X).
  • the thickness of the blade is less than or equal to about 1 mm, advantageously less than or equal to 3/10 th of a millimeter.
  • valve (1) All the elements forming the valve (1) are made of material from each other, so that the valve is monobloc. Alternatively, the valve is composed of several different materials.
  • the first element (3) is said fixed because it allows the attachment of the valve (1) on the gas engine under pressure on which it is intended to be mounted.
  • the second element (5) is said to be mobile and is connected to the first element by the first series of tongues (9).
  • the tongues (9) are of substantially spiral shape and wrap around the axis (X) of the valve (1).
  • the tabs (9) are uniformly distributed over an outer circumference of the second movable member
  • the tongues (9) are derived from materials of the movable element (5) and the fixed element
  • the cutouts (11) thus produced have, themselves, a spiral shape, wrapping around the axis (X) of the valve (1).
  • Each of the spiral cuts (11) has, in a clockwise direction, a first outer end (120) which is located at an inner circumference of the first fixed member (3), followed by a winding around and to the axis (X) of the valve (1) to terminate at a second end (121), which is substantially on an outer circumference of the second movable member
  • each cut (11) delimits, in a first half approximately, an outer edge of a first tongue (9) and, in a second half about, an inner edge of a second tongue (9) successive to the first tongue (9).
  • a flare (91) and (92) forming the ends of the tongues (9).
  • the third element (7) which is also mobile, is connected to the second movable element (5) by the second set of tongues (13) which came from both the third element mobile (7) and the second movable element (5).
  • the series of tabs which came from both the third element mobile (7) and the second movable element (5).
  • (13) are at a number of three, uniformly distributed over an outer circumference of the third movable member (7) and an inner circumference of the second movable member (5), and are made from a series of spiral cuts (15) around and towards the axis (X) made in the blade forming the valve
  • the valve (1) is substantially flat as shown in Figure 2a.
  • the second series of tongues 13 is initially deformed, then the first series of tongues (9) is deformed, so the valve has in section the shape illustrated in Figure 2b, the third movable element (7 ), the second movable element (5) and the first fixed element (3) being each in a plane, the three planes being substantially parallel to each other and perpendicular substantially to the axis (X) of the valve (1).
  • the pressurized gas engine (20) has a piston (21) connected by a link (23) to a camshaft (24).
  • the piston (21) is slidable along an axis, here vertical in the figures, in a cylinder (22) closed on the top by a yoke plate (27).
  • the piston (21) has on an upper face a compression spring (26), here a coil spring.
  • the motor (20) has above the yoke plate (27) a compression chamber (25) adapted to contain, during operation of the engine (20), a hot gas under pressure.
  • the yoke plate (27) has a first communicating passage (28) formed of a series of openings between the pressure chamber (25) and the cylinder (22) and a second communicating passage (29).
  • the second communicating passage (29) is formed of a substantially cylindrical opening of cylindrical shape and is opposite the compression spring (26). It is able to receive a free end of this compression spring (26) during operation of the gas engine under pressure (20).
  • the valve (1) according to the invention is mounted on a face of the yoke plate (27) delimiting the compression chamber (25). In the rest position, as illustrated in FIG.
  • the second movable element (3) closes the first communicating passage (28) while the second movable element (7) closes the second communicating passage (29), the first element fixed (3) being fixed by means known per se on the plate forming cylinder head (27) or crimped in vertical walls delimiting the compression chamber (25).
  • This deformation of the compression spring (26) is made possible because the existing pressure in the compression chamber (25) applies the inlet valve (1) against the yoke plate (27).
  • the force generated by this pressure on the third movable element (7) (this force has a value equal to the pressure multiplied by the surface of the third movable element (7)) is greater than the opposite force exerted by the compression spring (26) during its compression.
  • the force exerted by the latter on the third movable element (7) becomes greater than the force exerted by the pressure in the compression chamber (25) on the same third element mobile (7). Then, the compression spring (26) lifts the third movable member
  • the compression spring (26) As the piston continues its downward movement, the compression spring (26) is in a relaxed rest position. Therefore, the free end of the spring (26) in contact with the third movable member (7) follows the movement of the piston and back down into the second communicating passage (28) under the biasing forces due to the deformed tongues (13), on the one hand, and (9) on the other hand.
  • the second (5) and third (7) movable elements of the valve (1) perform the same movement and are successively plated and respectively on the first communicating passage (28) and the second communicating passage (29), closing the latter. Therefore, no flow (G) of hot gas under pressure exists between the compression chamber (25) and the variable volume chamber.
  • variable volume chamber (30) expands and the piston (21) continues its descent until reaching a bottom dead point which will trigger the start of the exhaust phase described below. .
  • valve (1) Once the valve (1) has closed the communicating passages (28) and (29), the latter remains pressed in the closed position under the effect of the pressure difference that exists between the pressure prevailing in the compression chamber ( 25) and the lower pressure prevailing in the variable volume chamber (30).
  • the only amount of energy required to move the intake valve (1) is the energy required to deform the compression spring (26) to contiguous turns. It should be noted that this energy necessary to deform up to contiguous turns the compression spring (26) is very low compared to the energy required to implement camshafts coming to press valves as in the US document 2005/0257523.
  • the exhaust valve (40) is, in principle, similar to the intake valve (1) which has just been described.
  • the exhaust valve (40) is generally substantially of revolution and is in the form of a thin blade.
  • the thickness of the blade is less than or equal to about 1 mm, advantageously less than or equal to 3/10 th of a millimeter.
  • the exhaust valve (40) has a first fixed element (42) whose role is similar to the first fixed element (3) of the inlet valve (1) described above.
  • the exhaust valve (40) has a second movable member (41) whose role is similar to the second movable member (5) of the intake valve (1).
  • a series of tabs (43) connects the first movable member (42) to the second movable member (41).
  • the embodiment of the tabs (43) is similar to that of the tabs (15) and (9) that we have described for the intake valve (1).
  • the noticeable difference between the intake valve (1) and the intake valve (40) is that at rest the exhaust valve is in the open position as shown in FIG. 4, i.e. that the second element
  • the yoke plate (27) has a series of orifices (44) forming a communicating passage between the variable volume chamber (30) and the exhaust duct (50). These openings (44) are uniformly distributed over a circumference and are opposite the movable member (41) of the exhaust valve (40). It should be noted that the orifices (28) forming the first communicating intake passage are themselves uniformly distributed over a circumference and facing the second movable element (5) of the intake valve as shown in FIG. 5).
  • the piston (21) is equipped with a support spring (45) whose constitution here is similar to that of the exhaust valve (40). Indeed, the support spring (45) has a first fixed element (47) adapted to allow the attachment of the support spring
  • the second movable element (46) of the support spring (45) is connected to the first fixed element (47) of the support spring (45) by a series of spiral tongues (48) similar to the spiral tongues (43) of the exhaust valve (40).
  • the pressure in the variable volume chamber (30) is greater than the existing pressure in the exhaust duct (50) to which the orifices (44) provide access.
  • This pressure difference makes it possible to keep the second movable element (41) pressed onto the yoke plate 27 closing the orifices (44) in the closed position, in spite of the return forces. exerted by the tabs (43) then elastically deformed.
  • This orifice (52) is connected to a pipe (51) which leads, in its upper part, to the exhaust duct.
  • the tubing (51) establishes a so-called load shedding circuit. Therefore, thanks to this unloading circuit, the pressure in the variable volume chamber (30) becomes equal to the pressure in the exhaust pipe, beyond the openings (44).
  • the second movable element (41) of the exhaust valve (40) is "peeled off” from the yoke plate (27) thus opening the openings (44) that will evacuate the gas contained in the variable volume chamber (30) during an ascent to the top dead center of the piston (21).
  • variable volume chamber during an intake phase may fluctuate around an ideal rate that avoids halting the fuel cycle. engine operation.
  • the use of an exhaust valve according to the invention makes it possible to "erase” and to overcome these possible fluctuations:
  • the opening of the exhaust valve according to the invention occurs before the bottom dead center of the piston. This avoids generating, at the end of the stroke of the expansion cycle, a vacuum in the variable volume chamber opposite the movement of the piston and therefore energy consuming. •
  • the unloading circuit allows an opening of the exhaust valve according to the invention in the bottom dead center position of the piston which avoids halting the operation of the cycle.
  • the inlet valve (100) of this embodiment differs from the inlet valve (1) previously described by the presence of a series of orifices (101) uniformly distributed over a circumference of the second movable member of the intake valve (100). Between two successive orifices (101), the second movable element of the intake valve
  • the number of orifices (101) is identical to the number of orifices forming the first communicating passage (28) in the yoke plate (27). However, each orifice of the yoke plate (27) faces an arm (102) of the second movable member of the intake valve (100). Thus, when the second movable member of the intake valve (100) is pressed against the yoke plate (27), each arm (102) closes a corresponding orifice of the first communicating passage
  • the exhaust valve (110) of this embodiment differs from the exhaust valve (40) previously described by the presence of a series of apertures (111) uniformly distributed over a circumference second movable member of the exhaust valve (40).
  • an arm of material (112) is located between two orifices (111) consecutive.
  • the number of ports (111) is similar to the number of exhaust ports (44) provided in the cylinder head plate (27). However, each arm
  • valves according to the invention reconciles low energy expenditure to their implementation and optimization of gas flows. It is thus possible to achieve high engine speeds with a high efficiency of operation.
  • the difference in engine power involved in a conventional combustion engine and a gas engine under pressure may be a factor of ten. This factor exists between an explosion generating about 30 bars (in a combustion engine) and the expansion of compressed gas at 3 bars (in a gas engine under pressure). Since the pull of a loosely compressed gas is lower, the passive resistances related to friction, camshaft drive and the activation force of the valve springs rapidly take on significant proportions which can destroy the overall yield.
  • the distribution mechanism using valves according to the invention sets in motion small masses (the blade forming the valves according to the invention has a thickness less than or equal to 1 mm, advantageously less than or equal to 3 / 10th of a mm) retained by elastically deformable connecting means having low activation forces.
  • the reduction of moving masses allows response times compatible with high stress frequencies without oversizing the elastically deformable connecting means stiffness.
  • the maximum pressure prevails continuously in the supply duct.
  • the effort required to open a traditional intake valve is proportional to its surface.
  • the stepped opening of the intake valve according to the invention decreases the necessary activation energy while providing a large pressure gas flow from the compression chamber to the variable volume chamber. This helps to power the motor optimally by improving the filling rate at high speed.
  • the activation energy of a monolithic equivalent unstaged valve would be ten to thirty times greater. Thus, it makes it possible to increase the passage section of the gas independently of the force required to open the valve according to the invention. Which is impossible with a traditional valve.
  • valves according to the invention in a pressurized gas engine makes it possible to obtain high expansion efficiencies by minimizing the energies of activation of the distribution while being compatible with large gas flows facilitating the rise in temperature. engine speed without destroying the fill rate of the variable volume chamber.
  • the valves according to the invention work naturally in the direction of the gas flow: it is the difference in pressure between the two faces of the valve which conditions its opening or closing.
  • the valves according to the invention which then operate against the flow of gas and therefore against the pressure difference between the two faces of the valve.

Abstract

The system intended for a pressurized gas engine includes a variable-volume chamber and a valve (1) comprising a first fixed element (3) intended to allow fastening of the valve to the engine, a second moveable element (5) intended to shut off in a conditional manner a passage providing gas communication with the variable-volume chamber, and first elastically deformable coupling means (9) connecting the first and second elements together, the chamber additionally comprising means for operating the second and third moveable elements of the valve.

Description

SYSTEME A SOUPAPE A FAIBLE ENERGIE POUR MOTEUR A GAZ SOUS PRESSION LOW ENERGY VALVE SYSTEM FOR A PRESSURIZED GAS ENGINE
L' invention concerne un système comportant une soupape d'admission ou d'échappement pour un moteur à gaz sous pression.The invention relates to a system comprising an intake or exhaust valve for a gas engine under pressure.
Par définition, un moteur à gaz sous pression est un moteur de détente où une pression maximum règne de façon sensiblement continue dans un conduit d'admission ou d'alimentation du moteur. Une réalisation particulière d'un tel moteur à gaz sous pression est un moteur à gaz chaud de type Ericsson. Le document US 2005/0257523 décrit un moteur à gaz chaud de type Ericsson comportant une soupape d'admission et une soupape d'échappement comprenant toutes deux une tête plate de forme circulaire montée à l'extrémité d'une tige de forme sensiblement cylindrique. L'ouverture et la fermeture de l'échappement ainsi que de l'admission par ces soupapes s'effectue en utilisant un arbre à came, associé à chacune des soupapes, venant appuyer sur l'extrémité opposée à la tête plate de la tige cylindrique de chacune des soupapes. La mise en mouvement de ces arbres à came est effectuée à partir du mouvement de rotation du vilebrequin du moteur Ericsson. Cela nécessite des liaisons mécaniques entre les arbres à came et le vilebrequin. L'inconvénient d'un tel système est qu'une très grande partie de l'énergie fournit par le moteur Ericsson est nécessaire pour venir ouvrir et fermer alternativement les soupapes d'admission et d'échappement. Cette énergie consommée abaisse drastiquement le rendement d'un tel moteur.By definition, a pressurized gas engine is an expansion motor where a maximum pressure prevails substantially continuously in an intake duct or motor supply. A particular embodiment of such a pressurized gas engine is an Ericsson type hot gas engine. US 2005/0257523 discloses an Ericsson type hot gas engine having an intake valve and an exhaust valve both having a circular shaped flat head mounted at the end of a substantially cylindrical rod. The opening and closing of the exhaust and of the intake by these valves is effected by using a camshaft associated with each of the valves, pressing on the end opposite to the flat head of the cylindrical rod. of each of the valves. The camshafts are set in motion from the rotational movement of the crankshaft of the Ericsson engine. This requires mechanical links between the camshafts and the crankshaft. The disadvantage of such a system is that a very large part of the energy supplied by the Ericsson engine is needed to open and close alternately the intake valves and exhaust. This consumed energy drastically lowers the efficiency of such an engine.
Un des buts de l'invention est de fournir un système amélioré comprenant une soupape améliorée destinée, soit à l'admission, soit à l'échappement, pour un moteur à gaz sous pression qui soit peu consommateur d'énergie lors de son utilisation tout en permettant une circulation optimale du gaz sous pression mettant en œuvre le moteur.One of the aims of the invention is to provide an improved system comprising an improved valve for either the intake or the exhaust for a pressurized gas engine that consumes little energy when it is being used. by allowing an optimal circulation of the gas under pressure using the engine.
A cet effet, il est prévu, selon l'invention, un système destiné à un moteur à gaz sous pression comportant : - une chambre à volume variable; et, une soupape comprenant un premier élément fixe destiné à permettre une fixation de la soupape sur le moteur, un deuxième élément mobile destiné à obturer de manière conditionnelle un passage de communication du gaz avec la chambre à volume variable, des premiers moyens de liaison déformables élastiquement liant les premier et deuxième éléments ensembles, la chambre comportant, en outre, des moyens de mise en œuvre du deuxième élément mobile de la soupape.For this purpose, it is provided, according to the invention, a system for a gas engine under pressure comprising: - a variable volume chamber; and a valve comprising a first stationary member for enabling the valve to be attached to the engine, a second movable member for conditionally closing a gas communication passage with the variable volume chamber, first deformable connecting means elastically linking the first and second elements together, the chamber further comprising means for implementing the second movable member of the valve.
Avantageusement, mais facultativement, la soupape comprend l'une des caractéristiques suivantes : la soupape est monobloc ; - la soupape forme une lame sensiblement plane avant déformation ; la soupape est sensiblement de forme circulaire ; les premier et deuxième éléments sont en forme d' anneaux concentriques ; - au repos, les premier et deuxième éléments sont sensiblement dans un même plan ; au repos, les premier et deuxième éléments sont dans deux plans différents sensiblement parallèles entre eux ; - la soupape comporte un troisième élément mobile apte à obturer un deuxième passage de communication du gaz avec la chambre à volume variable et des deuxièmes moyens de liaisons déformables élastiquement liant les deuxième et troisième éléments entre eux ; le troisième élément est en forme de disque sensiblement plan ; les premiers et/ou deuxièmes moyens de liaisons déformables élastiquement comportent des languettes ; les languettes sont de forme sensiblement spiralée et uniformément réparties sur une circonférence de la soupape ; les moyens de mise en œuvre sont destinés à mettre en œuvre le troisième élément mobile de la soupape ; les moyens de mise en œuvre comportent un élément déformable élastiquement monté sur un piston délimitant la chambre à volume variable ; - l'élément déformable élastique est de type ressort de compression. II est également prévu, selon l' invention, un moteur à gaz sous pression comportant au moins une soupape présentant au moins une des caractéristiques précédentes .Advantageously, but optionally, the valve comprises one of the following features: the valve is monobloc; the valve forms a substantially flat blade before deformation; the valve is substantially circular in shape; the first and second elements are in the form of concentric rings; at rest, the first and second elements are substantially in the same plane; at rest, the first and second elements are in two different planes substantially parallel to each other; - The valve comprises a third movable member adapted to close a second gas communication passage with the variable volume chamber and second resiliently deformable connecting means connecting the second and third elements together; the third element is substantially planar disc shape; the first and / or second elastically deformable connecting means comprise tabs; the tongues are of substantially spiral shape and uniformly distributed over a circumference of the valve; the implementation means are intended to implement the third movable member of the valve; the implementation means comprise an elastically deformable element mounted on a piston delimiting the variable volume chamber; the elastic deformable element is of the compression spring type. According to the invention, a pressurized gas engine comprising at least one valve having at least one of the preceding characteristics is also provided.
D'autres caractéristiques et avantages de l'invention apparaîtront lors de la description, ci- après, d'un mode de réalisation d'une soupape d'admission, puis d'une soupape d'échappement, ainsi que d'une variante de réalisation. Aux dessins annexés : la figure 1 est une vue tridimensionnelle d'une soupape d'admission selon un mode de réalisation de l'invention ; la figure 2a est une vue en coupe selon II-II de la soupape de la figure 1 au repos ; la figure 2b est une vue en coupe selon II-II de la soupape de la figure 1 en position ouverte ; - les figures 3a à 3d sont des vues en coupe schématiques simplifiées d'un moteur à gaz sous pression illustrant les étapes d' admission du gaz chaud sous pression dans la chambre à volume variable selon l'invention ; - la figure 4 est une vue tridimensionnelle en demi-coupe d'un cylindre d'un moteur à gaz sous pression illustrant une soupape d'échappement selon l'invention ; la figure 5 est une vue tridimensionnelle de dessus du cylindre de la figure 4 ; la figure 6 est une vue tridimensionnelle partielle éclatée illustrant une variante de réalisation de la soupape d' admission et de la soupape d'échappement, toutes deux selon l' invention .Other features and advantages of the invention will become apparent from the following description of an embodiment of an intake valve, then of an exhaust valve, as well as a variant of production. In the accompanying drawings: FIG. 1 is a three-dimensional view of an intake valve according to one embodiment of the invention; Figure 2a is a sectional view along II-II of the valve of Figure 1 at rest; Figure 2b is a sectional view along II-II of the valve of Figure 1 in the open position; - Figures 3a to 3d are simplified schematic sectional views of a pressurized gas engine illustrating the steps of admission of the hot gas under pressure in the variable volume chamber according to the invention; FIG. 4 is a three-dimensional, half-sectional view of a cylinder of a gas engine under pressure illustrating an exhaust valve according to the invention; Figure 5 is a three-dimensional top view of the cylinder of Figure 4; Figure 6 is an exploded partial three-dimensional view illustrating an alternative embodiment of the intake valve and the exhaust valve, both according to the invention.
En référence aux figures 1 à 2b, nous allons décrire une soupape d'admission (1) selon l'invention. La soupape (1) se présente, ici, sous la forme d'une lame de faible épaisseur et de forme de révolution autour d'un axe (X) . Par exemple, l'épaisseur de la lame est inférieure ou égale à 1 mm environ, avantageusement inférieure ou égale à 3/10eme de mm.Referring to Figures 1 to 2b, we will describe an intake valve (1) according to the invention. The valve (1) is here in the form of a thin blade and a shape of revolution about an axis (X). For example, the thickness of the blade is less than or equal to about 1 mm, advantageously less than or equal to 3/10 th of a millimeter.
Elle comporte, en partant d'une périphérie externe vers le centre, un premier élément en forme sensiblement d'anneau (3), puis d'une série de languettes (9), puis d'un deuxième élément en forme d'anneau (5), puis une deuxième série de languettes (13) et enfin d'un troisième élément (7) central de forme sensiblement d'un disque .It comprises, starting from an outer periphery towards the center, a first substantially ring-shaped element (3), then a series of tongues (9), then a second ring-shaped element ( 5), then a second series of tabs (13) and finally a third element (7) substantially shaped disc.
L'ensemble des éléments formant la soupape (1) est venu de matière des uns et des autres, de sorte que la soupape soit monobloc. En variante, la soupape est composée de plusieurs matériaux différents.All the elements forming the valve (1) are made of material from each other, so that the valve is monobloc. Alternatively, the valve is composed of several different materials.
Le premier élément (3) est dit fixe car il permet la fixation de la soupape (1) sur le moteur à gaz sous pression sur lequel elle est destinée à être montée. Le deuxième élément (5) est dit mobile et est lié au premier élément par la première série de languettes (9) . Les languettes (9) sont de forme sensiblement spiralée et s'enroulent autour de l'axe (X) de la soupape (1) .The first element (3) is said fixed because it allows the attachment of the valve (1) on the gas engine under pressure on which it is intended to be mounted. The second element (5) is said to be mobile and is connected to the first element by the first series of tongues (9). The tongues (9) are of substantially spiral shape and wrap around the axis (X) of the valve (1).
Ici, les languettes (9) sont uniformément réparties sur une circonférence extérieure du deuxième élément mobileHere, the tabs (9) are uniformly distributed over an outer circumference of the second movable member
(5) et sur une circonférence intérieure du premier élément fixe (3), les languettes (9) sont issues de matières de l'élément mobile (5) et de l'élément fixe(5) and on an inner circumference of the first fixed element (3), the tongues (9) are derived from materials of the movable element (5) and the fixed element
(3) . Elles sont réalisées par découpe de la lame formant la soupape (1) . Les découpes (11) ainsi réalisées ont, elles-mêmes, une forme spiralée, s' enroulant autour de l'axe (X) de la soupape (1) . Chacune des découpes spiralées (11) présente, dans le sens des aiguilles d'une montre, une première extrémité externe (120) qui se situe au niveau d'une circonférence interne du premier élément fixe (3), suivie d'un enroulement autour et vers l'axe (X) de la soupape (1) pour se terminer par une deuxième extrémité (121) , qui se situe sensiblement sur une circonférence externe du deuxième élément mobile(3). They are made by cutting the blade forming the valve (1). The cutouts (11) thus produced have, themselves, a spiral shape, wrapping around the axis (X) of the valve (1). Each of the spiral cuts (11) has, in a clockwise direction, a first outer end (120) which is located at an inner circumference of the first fixed member (3), followed by a winding around and to the axis (X) of the valve (1) to terminate at a second end (121), which is substantially on an outer circumference of the second movable member
(5) . Ainsi, chaque découpe (11) délimite, dans une première moitié environ, un bord externe d'une première languette (9) puis, dans une deuxième moitié environ, un bord interne d'une deuxième languette (9) successive à la première languette (9) . Enfin, au niveau des extrémités (120) et (121) de chacune des découpes spiralées (11), il est aménagé un évasement (91) et (92) formant les extrémités des languettes (9) . Cet évasement permet de mieux répartir les contraintes qui sont susceptibles d'apparaître lors d'une déformation de ces languettes, déformation survenant lors de l'ouverture de la soupape d'admission (1) comme cela sera décrit ultérieurement. De manière tout à fait similaire, le troisième élément (7), qui est lui aussi mobile, est relié au deuxième élément mobile (5) par la deuxième série de languettes (13) qui sont venues de matière à la fois avec le troisième élément mobile (7) et le deuxième élément mobile (5) . De même, ici, la série de languettes(5). Thus, each cut (11) delimits, in a first half approximately, an outer edge of a first tongue (9) and, in a second half about, an inner edge of a second tongue (9) successive to the first tongue (9). Finally, at the ends (120) and (121) of each of the spiral cuts (11), there is arranged a flare (91) and (92) forming the ends of the tongues (9). This flaring makes it possible to better distribute the stresses that are likely to appear during a deformation of these tongues, deformation occurring during the opening of the intake valve (1) as will be described later. In a very similar manner, the third element (7), which is also mobile, is connected to the second movable element (5) by the second set of tongues (13) which came from both the third element mobile (7) and the second movable element (5). Similarly, here the series of tabs
(13) sont aux nombres de trois, uniformément réparties sur une circonférence extérieure du troisième élément mobile (7) et sur une circonférence intérieure du deuxième élément mobile (5) , et sont réalisées à partir d'une série de découpes (15) spiralées autour et vers l'axe (X) réalisées dans la lame formant la soupape(13) are at a number of three, uniformly distributed over an outer circumference of the third movable member (7) and an inner circumference of the second movable member (5), and are made from a series of spiral cuts (15) around and towards the axis (X) made in the blade forming the valve
(1) . La réalisation des découpes (15) est similaire à la réalisation des découpes (11) précédemment décrite. Au repos, la soupape (1) est sensiblement plane comme cela est illustré à la figure 2a. Lors de l'ouverture, la deuxième série de languettes 13 est dans un premier temps déformée, puis la première série de languettes (9) est déformée, ainsi la soupape présente en coupe la forme illustrée en figure 2b, le troisième élément mobile (7), le deuxième élément mobile (5) et le premier élément fixe (3) se trouvant chacun dans un plan, les trois plans étant sensiblement parallèles entre eux et perpendiculaires sensiblement à l'axe (X) de la soupape (1) .(1). The making of the cuts (15) is similar to the production of the cuts (11) described above. At rest, the valve (1) is substantially flat as shown in Figure 2a. When opening, the second series of tongues 13 is initially deformed, then the first series of tongues (9) is deformed, so the valve has in section the shape illustrated in Figure 2b, the third movable element (7 ), the second movable element (5) and the first fixed element (3) being each in a plane, the three planes being substantially parallel to each other and perpendicular substantially to the axis (X) of the valve (1).
En référence aux figures 3a à 3d, nous allons décrire le fonctionnement de la soupape d'admission (1) qui vient d'être décrite. En remarque liminaire, il est à noter que dans les illustrations des figures 3a à 3d, l'échappement a été omis afin de simplifier la représentation et de bien décrire l'admission dans un moteur à gaz sous pression équipé d'une soupape d'admission selon l'invention décrite ci-dessus. Le moteur à gaz sous pression (20) comporte un piston (21) lié par une biellette (23) à un arbre à came (24) . Le piston (21) est apte à coulisser selon un axe, ici vertical sur les figures, dans un cylindre (22) fermé sur le dessus par une plaque formant culasse (27) . Le piston (21) comporte sur une face supérieure un ressort de compression (26), ici un ressort à boudin. Le moteur (20) comporte au dessus de la plaque formant culasse (27) une chambre de compression (25) apte à contenir, lors d'un fonctionnement du moteur (20), un gaz chaud sous pression. La plaque formant culasse (27) comporte un premier passage communicant (28), formé d'une série d'ouvertures, entre la chambre de pression (25) et le cylindre (22) ainsi qu'un deuxième passage communicant (29) . Le deuxième passage communicant (29) est formé d'une ouverture de forme cylindrique sensiblement de révolution et se trouve en regard du ressort de compression (26) . Il est apte à recevoir une extrémité libre de ce ressort de compression (26) lors d'un fonctionnement du moteur à gaz sous pression (20) . La soupape (1) selon l'invention est montée sur une face de la plaque formant culasse (27) délimitant la chambre de compression (25) . En position de repos, comme cela est illustré dans la figure 3a, le deuxième élément mobile (3) ferme le premier passage communicant (28) alors que le deuxième élément mobile (7) ferme le deuxième passage communicant (29), le premier élément fixe (3) étant fixé par des moyens connus en soi sur la plaque formant culasse (27) ou bien serti dans des parois verticales délimitant la chambre de compression (25) .Referring to Figures 3a to 3d, we will describe the operation of the inlet valve (1) just described. As a preliminary remark, it should be noted that in the illustrations of FIGS. 3a to 3d, the escapement has been omitted in order to simplify the representation and to describe the admission in a gas engine under pressure equipped with an intake valve according to the invention described above. The pressurized gas engine (20) has a piston (21) connected by a link (23) to a camshaft (24). The piston (21) is slidable along an axis, here vertical in the figures, in a cylinder (22) closed on the top by a yoke plate (27). The piston (21) has on an upper face a compression spring (26), here a coil spring. The motor (20) has above the yoke plate (27) a compression chamber (25) adapted to contain, during operation of the engine (20), a hot gas under pressure. The yoke plate (27) has a first communicating passage (28) formed of a series of openings between the pressure chamber (25) and the cylinder (22) and a second communicating passage (29). The second communicating passage (29) is formed of a substantially cylindrical opening of cylindrical shape and is opposite the compression spring (26). It is able to receive a free end of this compression spring (26) during operation of the gas engine under pressure (20). The valve (1) according to the invention is mounted on a face of the yoke plate (27) delimiting the compression chamber (25). In the rest position, as illustrated in FIG. 3a, the second movable element (3) closes the first communicating passage (28) while the second movable element (7) closes the second communicating passage (29), the first element fixed (3) being fixed by means known per se on the plate forming cylinder head (27) or crimped in vertical walls delimiting the compression chamber (25).
Lors d'un fonctionnement du moteur à gaz sous pression (20), lorsque le piston (21) remonte dans le cylindre (22) en fin de phase d'échappement qui sera décrite ultérieurement, l'extrémité libre du ressortDuring operation of the gas engine under pressure (20), when the piston (21) back in the cylinder (22) at the end of the exhaust phase which will be described later, the free end of the spring
(26) pénètre dans le deuxième passage communicant (29) et vient en appui contre le troisième élément mobile (7) de la soupape (1) . Le piston continuant son mouvement vers le haut jusqu'à son point mort haut, le ressort de compression (26) est comprimé jusqu'à ce que ses spires deviennent jointives.(26) enters the second communicating passage (29) and bears against the third movable element (7) of the valve (1). As the piston continues its upward movement to its top dead center, the compression spring (26) is compressed until its turns become contiguous.
Cette déformation du ressort de compression (26) est rendue possible car la pression existante dans la chambre de compression (25) applique la soupape d'admission (1) contre la plaque formant culasse (27) . L'effort généré par cette pression sur le troisième élément mobile (7) (cet effort a une valeur égale à la pression que multiplie la surface du troisième élément mobile (7)) est supérieur à l'effort opposé exercé par le ressort de compression (26) lors de sa compression. Une fois que le ressort est comprimé à spires jointives, l'effort exercé par ce dernier sur le troisième élément mobile (7) devient supérieur à l'effort exercé par la pression régnant dans la chambre de compression (25) sur ce même troisième élément mobile (7) . Alors, le ressort de compression (26) soulève le troisième élément mobileThis deformation of the compression spring (26) is made possible because the existing pressure in the compression chamber (25) applies the inlet valve (1) against the yoke plate (27). The force generated by this pressure on the third movable element (7) (this force has a value equal to the pressure multiplied by the surface of the third movable element (7)) is greater than the opposite force exerted by the compression spring (26) during its compression. Once the spring is compressed to contiguous turns, the force exerted by the latter on the third movable element (7) becomes greater than the force exerted by the pressure in the compression chamber (25) on the same third element mobile (7). Then, the compression spring (26) lifts the third movable member
(7) en déformant de manière élastique les languettes (13) alors que le deuxième élément mobile (5) reste plaqué contre la plaque formant culasse (27) par la pression régnant dans la chambre de compression (25) , gardant fermé le premier passage communicant (28) . Cette phase de l'admission est illustré en figure 3b. une fois que le troisième élément mobile (7) se soulève, un flux(7) elastically deforming the tabs (13) while the second movable member (5) remains pressed against the yoke plate (27) by the pressure in the compression chamber (25), keeping the first communicating passage closed (28). This phase of admission is illustrated in Figure 3b. once the third movable element (7) is lifted, a flow
(G) de gaz chaud sous pression s'établit autour des découpes (15) des lames (13) puis pénètre dans le passage communicant (29) . Dès lors, la pression régnant dans la chambre de compression (25) vient appuyer sur le piston (21) au regard du deuxième passage communicant(G) pressurized hot gas is established around the cutouts (15) of the blades (13) and enters the communicating passage (29). Therefore, the pressure in the compression chamber (25) presses on the piston (21) with respect to the second communicating passage
(29), obligeant ce dernier à débuter un mouvement de descente dans le cylindre (22) et l'établissement d'une chambre à volume variable (30) . Dès lors, au niveau du premier passage communicant (28), de part et d'autre du deuxième élément mobile (25) règne la même pression. D'une part le ressort (26) continue à revenir vers sa position de repos tout en poussant vers le haut sur le troisième élément mobile (7) (la même pression s 'exerçant de part et d'autre du troisième élément mobile) qui lui-même entraine alors dans son mouvement le deuxième élément (5) causant l'ouverture du premier passage communicant (28), ce qui permet d'augmenter le flux (G) de gaz chaud de la chambre de compression (25) vers la chambre à volume variable (30) située entre la plaque formant culasse (27) et la face supérieure du piston (21) . Cette situation est illustrée en figure 3c. Le piston continuant son mouvement de descente, le ressort de compression (26) se retrouve dans une position détendue de repos. Dès lors, l'extrémité libre du ressort (26) au contact avec le troisième élément mobile (7) suit le mouvement du piston et redescend dans le deuxième passage communicant (28) sous les efforts de rappel dus aux languettes déformées (13), d'une part, et (9), d'autre part. Les deuxième (5) et troisième (7) éléments mobiles de la soupape (1) effectuent le même mouvement et viennent se plaquer successivement et respectivement sur le premier passage communicant (28) et le deuxième passage communicant (29), fermant ces derniers. Dès lors, aucun flux (G) de gaz chaud sous pression n'existe entre la chambre de compression (25) et la chambre à volume variable. Cependant, le gaz chaud sous pression introduit dans la chambre de volume variable (30) se détend et le piston (21) continue sa descente jusqu'à atteindre un point mort bas qui déclenchera le début de la phase d'échappement décrite ci-dessous. Une fois que la soupape (1) a refermé les passages communicants (28) et (29), celle-ci reste plaquée en position fermée sous l'effet de la différence de pression qui existe entre la pression régnante dans la chambre de compression (25) et la pression, inférieure, régnante dans la chambre à volume variable (30) .(29), causing the latter to begin a descent movement in the cylinder (22) and the establishment of a variable volume chamber (30). Therefore, at the first communicating passage (28), on both sides of the second movable member (25) reigns the same pressure. On the one hand the spring (26) continues to return to its rest position while pushing upward on the third movable element (7) (the same pressure exerted on either side of the third movable element) which itself then causes in its movement the second element (5) causing the opening of the first communicating passage (28), which increases the flow (G) of hot gas from the compression chamber (25) to the variable volume chamber (30) located between the yoke plate (27) and the upper face of the piston (21). This situation is illustrated in Figure 3c. As the piston continues its downward movement, the compression spring (26) is in a relaxed rest position. Therefore, the free end of the spring (26) in contact with the third movable member (7) follows the movement of the piston and back down into the second communicating passage (28) under the biasing forces due to the deformed tongues (13), on the one hand, and (9) on the other hand. The second (5) and third (7) movable elements of the valve (1) perform the same movement and are successively plated and respectively on the first communicating passage (28) and the second communicating passage (29), closing the latter. Therefore, no flow (G) of hot gas under pressure exists between the compression chamber (25) and the variable volume chamber. However, the hot pressurized gas introduced into the variable volume chamber (30) expands and the piston (21) continues its descent until reaching a bottom dead point which will trigger the start of the exhaust phase described below. . Once the valve (1) has closed the communicating passages (28) and (29), the latter remains pressed in the closed position under the effect of the pressure difference that exists between the pressure prevailing in the compression chamber ( 25) and the lower pressure prevailing in the variable volume chamber (30).
D'un point de vue énergétique, la seule quantité d'énergie nécessaire pour mettre en mouvement la soupape d'admission (1) est l'énergie nécessaire à déformer jusqu'à spires jointives le ressort de compression (26) . Il est à noter que cette énergie nécessaire à déformer jusqu'à spires jointives le ressort de compression (26) est très faible par rapport à l'énergie nécessaire pour mettre en œuvre des arbres à came venant appuyer sur des soupapes comme dans le document US 2005/0257523.From an energy point of view, the only amount of energy required to move the intake valve (1) is the energy required to deform the compression spring (26) to contiguous turns. It should be noted that this energy necessary to deform up to contiguous turns the compression spring (26) is very low compared to the energy required to implement camshafts coming to press valves as in the US document 2005/0257523.
En référence à la figure 4, nous allons décrire une soupape d'échappement selon l'invention ainsi que la phase d'échappement. La soupape d'échappement (40) est, sur le principe, similaire à la soupape d'admission (1) qui vient d'être décrite. La soupape d'échappement (40) est de forme générale sensiblement de révolution et se présente sous la forme d'une lame de faible épaisseur. Par exemple, l'épaisseur de la lame est inférieure ou égale à 1 mm environ, avantageusement inférieure ou égale à 3/10eme de mm. La soupape d'échappement (40) comporte un premier élément fixe (42) dont le rôle est similaire au premier élément fixe (3) de la soupape d'admission (1) précédemment décrite. De même, la soupape d'échappement (40) présente un deuxième élément mobile (41) dont le rôle est similaire au deuxième élément mobile (5) de la soupape d'admission (1) . Et de manière similaire, une série de languettes (43) relie le premier élément mobile (42) au deuxième élément mobile (41) . La réalisation des languettes (43) est similaire à celle des languettes (15) et (9) que nous avons décrites pour la soupape d'admission (1) . La différence notable entre la soupape d'admission (1) et la soupape d'admission (40) est qu'au repos, la soupape d'échappement est en position ouverte comme illustré dans la figure 4, c'est-à-dire que le deuxième élémentWith reference to FIG. 4, we will describe an exhaust valve according to the invention as well as the exhaust phase. The exhaust valve (40) is, in principle, similar to the intake valve (1) which has just been described. The exhaust valve (40) is generally substantially of revolution and is in the form of a thin blade. For example, the thickness of the blade is less than or equal to about 1 mm, advantageously less than or equal to 3/10 th of a millimeter. The exhaust valve (40) has a first fixed element (42) whose role is similar to the first fixed element (3) of the inlet valve (1) described above. Similarly, the exhaust valve (40) has a second movable member (41) whose role is similar to the second movable member (5) of the intake valve (1). And similarly, a series of tabs (43) connects the first movable member (42) to the second movable member (41). The embodiment of the tabs (43) is similar to that of the tabs (15) and (9) that we have described for the intake valve (1). The noticeable difference between the intake valve (1) and the intake valve (40) is that at rest the exhaust valve is in the open position as shown in FIG. 4, i.e. that the second element
(41) qui forme un anneau sensiblement plan se trouve dans un plan différent et sensiblement parallèle à un plan contenant le premier élément fixe (42) lui-même en forme d'anneau sensiblement plan. Une fois découpées, les languettes (43) sont déformées de manières plastiques, afin que la soupape (40) présente cette configuration au repos. Comme cela est illustré à la figure 4, la plaque formant culasse (27) comporte une série d'orifices (44) formant un passage communicant entre la chambre à volume variable (30) et le conduit d'échappement (50) . Ces ouvertures (44) sont uniformément réparties sur une circonférence et se trouvent en regard de l'élément mobile (41) de la soupape d'échappement (40) . Il est à noter que les orifices (28) formant le premier passage communicant d'admission sont eux-mêmes uniformément répartis sur une circonférence et en regard du deuxième élément mobile (5) de la soupape d'admission comme cela est illustré en figure (5) . Le piston (21) est équipé d'un ressort d'appui (45) dont la constitution ici est similaire à celle de la soupape d'échappement (40) . En effet, le ressort d'appui (45) présente un premier élément fixe (47) apte à permettre la fixation du ressort d'appui(41) which forms a substantially planar ring is in a different plane and substantially parallel to a plane containing the first fixed element (42) itself substantially plane ring shape. Once cut, the tabs (43) are plastically deformed so that the valve (40) has this configuration at rest. As illustrated in Figure 4, the yoke plate (27) has a series of orifices (44) forming a communicating passage between the variable volume chamber (30) and the exhaust duct (50). These openings (44) are uniformly distributed over a circumference and are opposite the movable member (41) of the exhaust valve (40). It should be noted that the orifices (28) forming the first communicating intake passage are themselves uniformly distributed over a circumference and facing the second movable element (5) of the intake valve as shown in FIG. 5). The piston (21) is equipped with a support spring (45) whose constitution here is similar to that of the exhaust valve (40). Indeed, the support spring (45) has a first fixed element (47) adapted to allow the attachment of the support spring
(45) sur le piston (21) et d'un deuxième élément mobile(45) on the piston (21) and a second movable member
(46) qui, le ressort d'appui (45)une fois monté sur le piston (21), se trouve en regard du deuxième élément mobile (41) de la soupape d'échappement (40) . Le deuxième élément mobile (46) du ressort d'appui (45) est lié au premier élément fixe (47) du ressort d'appui (45) par une série de languettes spiralées (48) similaires aux languettes spiralées (43) de la soupape d'échappement (40) .(46) which, once mounted on the piston (21), the bearing spring (45) is opposite the second movable element (41) of the exhaust valve (40). The second movable element (46) of the support spring (45) is connected to the first fixed element (47) of the support spring (45) by a series of spiral tongues (48) similar to the spiral tongues (43) of the exhaust valve (40).
Nous allons maintenant décrire le fonctionnement de la soupape d'échappement (40) selon l'invention. Lors de la phase d'admission et de détente, la pression qui règne dans la chambre à volume variable (30) est supérieure à la pression existante dans le conduit d'échappement (50) auquel les orifices (44) donnent accès. Cette différence de pression permet de maintenir plaqué en position fermée le deuxième élément mobile (41) sur la plaque formant culasse 27 fermant les orifices (44) , et ce malgré les efforts de rappel exercés par les languettes (43) alors élastiquement déformées .We will now describe the operation of the exhaust valve (40) according to the invention. During the intake and expansion phase, the pressure in the variable volume chamber (30) is greater than the existing pressure in the exhaust duct (50) to which the orifices (44) provide access. This pressure difference makes it possible to keep the second movable element (41) pressed onto the yoke plate 27 closing the orifices (44) in the closed position, in spite of the return forces. exerted by the tabs (43) then elastically deformed.
Lorsque le piston, lors de la phase de détente suivant la phase d'admission, arrive dans sa position de point mort bas tel qu'illustré en figure 4, il provoque alors une communication de la chambre à volume variableWhen the piston, during the expansion phase following the intake phase, arrives in its low dead position as shown in Figure 4, it then causes a communication of the variable volume chamber
(30) avec un orifice (52) de la paroi du cylindre (22) .(30) with a hole (52) in the wall of the cylinder (22).
Cet orifice (52) est lié à une tubulure (51) qui mène, dans sa partie supérieure, au conduit d'échappement. La tubulure (51) établit un circuit dit de délestage. Dès lors, grâce à ce circuit de délestage, la pression régnant dans la chambre de volume variable (30) devient égale à la pression régnant dans le conduit d'échappement, au delà des ouvertures (44) . A ce moment, sous l'effet du rappel élastique des languettes spiralées (43) , le deuxième élément mobile (41) de la soupape d'échappement (40) est « décollé » de la plaque formant culasse (27) ouvrant ainsi les ouverture (44) qui permettront d'évacuer le gaz contenu dans la chambre de volume variable (30) lors d'une remontée vers le point mort haut du piston (21) . Avant que le piston (21) atteigne son point mort haut, signifiant le début du cycle d'admission qui a été décrit ci-dessus, l'élément mobile (46) du ressort d'appui (45) vient en contact avec l'élément mobile (41) de la soupape d'échappement (40), ce qui va permettre de venir plaquer de nouveau l'élément mobile (41) de la soupape d'échappement (40) sur la plaque formant culasse (27) afin de fermer les orifices (44) et ce jusqu'au début de la phase d'admission précédemment décrite. Nous rappelons que dès le début de cette phase d'admission, une pression équivalente à la pression établie dans la chambre de compression (25) s'établit dans la chambre à volume variable (30), pression largement suffisante pour maintenir alors fermée par l'élément mobile (41) de la soupape d'échappement (40) les orifices d'échappement (44) jusqu'à mise en œuvre du circuit de délestage (51), lorsque de nouveau le piston (21) atteindra de nouveau son point mort bas.This orifice (52) is connected to a pipe (51) which leads, in its upper part, to the exhaust duct. The tubing (51) establishes a so-called load shedding circuit. Therefore, thanks to this unloading circuit, the pressure in the variable volume chamber (30) becomes equal to the pressure in the exhaust pipe, beyond the openings (44). At that moment, under the effect of the elastic return of the spiral tongues (43), the second movable element (41) of the exhaust valve (40) is "peeled off" from the yoke plate (27) thus opening the openings (44) that will evacuate the gas contained in the variable volume chamber (30) during an ascent to the top dead center of the piston (21). Before the piston (21) reaches its top dead point, signifying the beginning of the intake cycle which has been described above, the movable member (46) of the support spring (45) comes into contact with the movable element (41) of the exhaust valve (40), which will allow to come again plating the movable element (41) of the exhaust valve (40) on the cylinder plate (27) to close the openings (44) until the beginning of the admission phase described above. We recall that from the beginning of this admission phase, a pressure equivalent to the pressure established in the chamber of compression (25) is established in the variable volume chamber (30), a pressure that is largely sufficient to keep the exhaust ports (44) closed until the exhaust valve (40) has closed implementing the load shedding circuit (51), when the piston (21) again reaches its bottom dead point.
D'un point de vue énergétique, la seule consommation d'énergie nécessaire pour mettre en œuvre cette soupape d'échappement (40) selon l'invention est l'énergie nécessaire à déformer les languettes spiraléesFrom an energy point of view, the only energy consumption required to implement this exhaust valve (40) according to the invention is the energy required to deform the spiral tongues
(43) de la soupape d'échappement (40), dépense d'énergie qui reste bien inférieure à la mise en œuvre d'un arbre à came comme pour le moteur à gaz chaud de type Ericsson décrit dans le document US2005/0257523.(43) of the exhaust valve (40), energy expenditure which remains much lower than the implementation of a camshaft as for the Ericsson type hot gas engine described in US2005 / 0257523.
Il est à noter qu'en fonction du régime moteur et des températures de fonctionnement, un taux de remplissage de la chambre à volume variable lors d'une phase d'admission peut fluctuer autour d'un taux idéal évitant d'enrayer le cycle de fonctionnement du moteur. L'utilisation d'une soupape d'échappement selon l'invention permet de « gommer » et de s'affranchir de ces éventuelles fluctuations:It should be noted that, depending on the engine speed and the operating temperatures, a filling rate of the variable volume chamber during an intake phase may fluctuate around an ideal rate that avoids halting the fuel cycle. engine operation. The use of an exhaust valve according to the invention makes it possible to "erase" and to overcome these possible fluctuations:
• dans le cas d'un sous remplissage de la chambre à volume variable, l'ouverture de la soupape d'échappement selon l'invention intervient avant le point mort bas du piston. Ceci évite de générer, en fin de course du cycle de détente, une dépression dans la chambre à volume variable opposée au mouvement du piston et donc consommatrice d' énergie . • dans le cas d'un remplissage trop important de la chambre à volume variable, le circuit de délestage permet une ouverture de la soupape d' échappement selon l'invention en position point mort bas du piston ce qui évite d'enrayer le fonctionnement du cycle .In the case of underfilling of the variable volume chamber, the opening of the exhaust valve according to the invention occurs before the bottom dead center of the piston. This avoids generating, at the end of the stroke of the expansion cycle, a vacuum in the variable volume chamber opposite the movement of the piston and therefore energy consuming. • In the case of excessive filling of the variable volume chamber, the unloading circuit allows an opening of the exhaust valve according to the invention in the bottom dead center position of the piston which avoids halting the operation of the cycle.
Ainsi, une stabilité de fonctionnement de l'échappement est donc assurée et son fonctionnement reste optimal quelques soit le taux de remplissage du cylindre .Thus, an operational stability of the exhaust is therefore ensured and its operation remains optimal regardless of the filling rate of the cylinder.
En référence à la figure 6, nous allons brièvement décrire une variante de réalisation à la fois de la soupape d'échappement selon l'invention et de la soupape d'admission toujours selon l'invention.Referring to Figure 6, we will briefly describe an alternative embodiment of both the exhaust valve according to the invention and the intake valve still according to the invention.
La soupape d'admission (100) de cette variante de réalisation se différencie de la soupape d'admission (1) précédemment décrite par la présence d'une série d'orifices (101) uniformément répartis sur une circonférence du deuxième élément mobile de la soupape d'admission (100) . Entre deux orifices successifs (101), le deuxième élément mobile de la soupape d'admissionThe inlet valve (100) of this embodiment differs from the inlet valve (1) previously described by the presence of a series of orifices (101) uniformly distributed over a circumference of the second movable member of the intake valve (100). Between two successive orifices (101), the second movable element of the intake valve
(100) présente un bras de matière (102) . Le nombre d'orifices (101) est identique au nombre d'orifices formant le premier passage communicant (28) dans la plaque formant culasse (27) . Toutefois, chaque orifice de la plaque formant culasse (27) est en regard d'un bras (102) du deuxième élément mobile de la soupape d'admission (100) . Ainsi, lorsque le deuxième élément mobile de la soupape d'admission (100) est plaqué contre la plaque formant culasse (27), chaque bras (102) ferme un orifice correspondant du premier passage communiquant(100) has a material arm (102). The number of orifices (101) is identical to the number of orifices forming the first communicating passage (28) in the yoke plate (27). However, each orifice of the yoke plate (27) faces an arm (102) of the second movable member of the intake valve (100). Thus, when the second movable member of the intake valve (100) is pressed against the yoke plate (27), each arm (102) closes a corresponding orifice of the first communicating passage
(28) . La présence des orifices (101) sur la soupape d'admission (100) permet d'optimiser au maximum le flux (G) de gaz chaud sous pression lors de l'ouverture de cette soupape d'admission (100), tout en allégeant la soupape en elle-même.(28). The presence of the orifices (101) on the intake valve (100) optimizes the maximum flow (G) of hot gas under pressure when opening the intake valve (100), while relieving the valve itself.
D'une manière similaire, la soupape d'échappement (110) de cette variante de réalisation se différencie de la soupape d'échappement (40) précédemment décrite par la présence d'une série d'ouverture (111) uniformément répartie sur une circonférence de deuxième élément mobile de la soupape d'échappement (40) . De même, un bras de matière (112) se situe entre deux orifices (111) consécutifs. Le nombre d'orifices (111) est similaire au nombre d'orifices d'échappement (44) aménagé dans la plaque formant culasse (27) . Toutefois, chaque brasIn a similar manner, the exhaust valve (110) of this embodiment differs from the exhaust valve (40) previously described by the presence of a series of apertures (111) uniformly distributed over a circumference second movable member of the exhaust valve (40). Similarly, an arm of material (112) is located between two orifices (111) consecutive. The number of ports (111) is similar to the number of exhaust ports (44) provided in the cylinder head plate (27). However, each arm
(112) se trouve en regard d'un orifice (44) correspondant. Ainsi, lorsque le deuxième élément mobile de la soupape d'échappement (110) est plaqué contre la plaque formant culasse (27), le bras (112) vient fermer l'orifice (44) associé. De même, la présence d'orifice(112) is opposite a corresponding orifice (44). Thus, when the second movable member of the exhaust valve (110) is pressed against the yoke plate (27), the arm (112) closes the orifice (44) associated. Similarly, the presence of orifice
(111) permet d'optimiser au maximum le flux d'échappement du gaz présent dans la chambre à volume variable lors de la phase d'échappement, tout en allégeant la soupape en elle-même.(111) maximizes the exhaust flow of gas present in the variable volume chamber during the exhaust phase, while reducing the valve itself.
Il est à noter que l'utilisation de soupapes selon l'invention dans un moteur à gaz sous pression permet de concilier faible dépense d'énergie à leur mise en œuvre et optimisation des flux de gaz. Il est ainsi possible d'atteindre de hautes vitesses de rotation du moteur avec un haut rendement de fonctionnement. Par exemple, la différence de puissance motrice mise en jeu dans un moteur à explosion traditionnel et un moteur à gaz sous pression peut-être d'un facteur dix. Ce facteur existe entre une explosion générant 30 bars environ ( dans un moteur à explosion) et la détente de gaz comprimé à 3 bars (dans un moteur à gaz sous pression) . La motricité de la détente d'un gaz faiblement comprimé étant moindre, les résistances passives liées au frottement, à l'entraînement d'arbres à cames et à l'effort d' activation des ressorts de soupapes prennent rapidement des proportions importantes pouvant détruire le rendement global. Comparer à une solution avec soupapes comme illustrée dans le document US2005/0257523, le mécanisme de distribution utilisant des soupapes selon l'invention met en mouvement de faibles masses (la lame formant les soupapes selon l' invention présente une épaisseur inférieure ou égale à 1 mm environ, avantageusement inférieure ou égale à 3/10eme de mm) retenues par des moyens de liaison déformables élastiquement présentant des efforts d' activation faibles. La diminution des masses en mouvement permet des temps de réponse compatibles avec de hautes fréquences de sollicitation sans surdimensionner les moyens de liaison déformables élastiquement en raideur. Ces considérations permettent de diminuer d'un facteur dix environ l'énergie d' activation de la distribution comparé à une solution à soupapes massives traditionnelle d'ouverture équivalente comme illustrée dans le document US2005/0257523. D'autre part, dans un moteur à gaz sous pression, la pression maximum règne de façon continue dans le conduit d'alimentation. Aussi l'effort nécessaire a l'ouverture d'une soupape d'admission traditionnelle est proportionnel à sa surface. L'ouverture étagée de la soupape d'admission selon l'invention diminue l'énergie d' activation nécessaire tout en offrant un flux de gaz sous pression important de la chambre de compression vers la chambre à volume variable. Ceci contribue à alimenter le moteur de façon optimal en améliorant le taux de remplissage à vitesse de rotation élevée. L'énergie d' activation d'une soupape non étagée monolithique équivalente serait dix à trente fois supérieure. Ainsi cela permet d'augmenter la section de passage du gaz indépendamment de l'effort à fournir pour ouvrir la soupape selon l'invention. Ce qui est impossible avec une soupape traditionnelle.It should be noted that the use of valves according to the invention in a pressurized gas engine reconciles low energy expenditure to their implementation and optimization of gas flows. It is thus possible to achieve high engine speeds with a high efficiency of operation. For example, the difference in engine power involved in a conventional combustion engine and a gas engine under pressure may be a factor of ten. This factor exists between an explosion generating about 30 bars (in a combustion engine) and the expansion of compressed gas at 3 bars (in a gas engine under pressure). Since the pull of a loosely compressed gas is lower, the passive resistances related to friction, camshaft drive and the activation force of the valve springs rapidly take on significant proportions which can destroy the overall yield. Compared to a solution with valves as illustrated in document US2005 / 0257523, the distribution mechanism using valves according to the invention sets in motion small masses (the blade forming the valves according to the invention has a thickness less than or equal to 1 mm, advantageously less than or equal to 3 / 10th of a mm) retained by elastically deformable connecting means having low activation forces. The reduction of moving masses allows response times compatible with high stress frequencies without oversizing the elastically deformable connecting means stiffness. These considerations make it possible to reduce by approximately a factor of 10 the activation energy of the distribution compared to a conventional massive valve solution of equivalent opening as illustrated in document US2005 / 0257523. On the other hand, in a gas engine under pressure, the maximum pressure prevails continuously in the supply duct. Also the effort required to open a traditional intake valve is proportional to its surface. The stepped opening of the intake valve according to the invention decreases the necessary activation energy while providing a large pressure gas flow from the compression chamber to the variable volume chamber. This helps to power the motor optimally by improving the filling rate at high speed. The activation energy of a monolithic equivalent unstaged valve would be ten to thirty times greater. Thus, it makes it possible to increase the passage section of the gas independently of the force required to open the valve according to the invention. Which is impossible with a traditional valve.
L'utilisation de soupapes selon l'invention dans un moteur à gaz sous pression permet d'obtenir de hauts rendements de détente par une minimisation des énergies d' activation de la distribution tout en étant compatible avec des flux de gaz importants facilitant la montée en régime du moteur sans détruire le taux de remplissage de la chambre à volume variable. II est a noter que les soupapes selon l'invention travaillent naturellement dans le sens du flux de gaz : c'est la différence de pression entre les deux faces de la soupape qui conditionne son ouverture ou sa fermeture. Ici dans la cadre des moteurs à gaz chaud, les soupapes selon l'invention qui fonctionnent alors à l' encontre du flux de gaz et donc à l' encontre de la différence de pression entres les deux faces de la soupape .The use of valves according to the invention in a pressurized gas engine makes it possible to obtain high expansion efficiencies by minimizing the energies of activation of the distribution while being compatible with large gas flows facilitating the rise in temperature. engine speed without destroying the fill rate of the variable volume chamber. It should be noted that the valves according to the invention work naturally in the direction of the gas flow: it is the difference in pressure between the two faces of the valve which conditions its opening or closing. Here in the context of hot gas engines, the valves according to the invention which then operate against the flow of gas and therefore against the pressure difference between the two faces of the valve.
Bien entendu, il est possible d'apporter de nombreuses modifications à l'invention sans pour autant sortir du cadre de celle-ci. Of course, it is possible to make numerous modifications to the invention without departing from the scope thereof.

Claims

REVENDICATIONS
1. Système destinée à un moteur à gaz sous pression (20), comportant : - une chambre à volume variable (30) ; et, une soupape (1, 40 ; 100, 110) comprenant un premier élément fixe (3, 42) destiné à permettre une fixation de la soupape sur le moteur, un deuxième élément mobile (5, 41) destiné à obturer de manière conditionnelle un passage de communication (28, 44) du gaz avec la chambre à volume variable, des premiers moyens de liaison déformables élastiquement (9, 43) liant les premier et deuxième éléments ensembles, caractérisé en ce que la chambre comporte, en outre, des moyens de mise en œuvre (26 ; 45) du deuxième élément mobile de la soupape.A system for a pressurized gas engine (20) comprising: - a variable volume chamber (30); and, a valve (1, 40; 100, 110) including a first stationary member (3, 42) for providing valve attachment to the engine, a second movable member (5, 41) for conditionally closing a communication passage (28, 44) of the gas with the variable volume chamber, first resiliently deformable connecting means (9, 43) connecting the first and second elements together, characterized in that the chamber further comprises means for implementing (26; 45) the second movable member of the valve.
2. Système selon la revendication 1, caractérisé en ce que la soupape est monobloc.2. System according to claim 1, characterized in that the valve is monobloc.
3. Système selon les revendications 1 ou 2, caractérisé en ce que la soupape forme une lame sensiblement plane avant déformation.3. System according to claims 1 or 2, characterized in that the valve forms a substantially flat blade before deformation.
4. Système selon l'une des revendications 1 à 3, caractérisé en ce que la soupape est sensiblement de forme circulaire. 4. System according to one of claims 1 to 3, characterized in that the valve is substantially circular in shape.
5. Système selon la revendication 4, caractérisé en ce que les premier et deuxième éléments sont en forme d'anneau concentrique.5. System according to claim 4, characterized in that the first and second elements are in the form of a concentric ring.
6. Système selon la revendication 5, caractérisé en ce que, au repos, les premier et deuxième éléments sont sensiblement dans un même plan.6. System according to claim 5, characterized in that, at rest, the first and second elements are substantially in the same plane.
7. Système selon la revendication 5, caractérisé en ce que, au repos, les premier et deuxième éléments sont dans deux plans différents sensiblement parallèles entre eux.7. System according to claim 5, characterized in that, at rest, the first and second elements are in two different planes substantially parallel to each other.
8. Système selon l'une des revendications 1 à 7, caractérisé en ce que la soupape comporte un troisième élément mobile (7) destiné à obturer un deuxième passage de communication (29) du gaz avec la chambre à volume variable (30) et des deuxièmes moyens de liaisons déformables (13) liant les deuxième et troisième éléments entre eux.8. System according to one of claims 1 to 7, characterized in that the valve comprises a third movable member (7) for closing a second communication passage (29) of the gas with the variable volume chamber (30) and second deformable link means (13) linking the second and third elements to each other.
9. Système selon la revendication 8, caractérisé en ce que le troisième élément est en forme de disque sensiblement .9. System according to claim 8, characterized in that the third element is disk-shaped substantially.
10. Système selon l'une des revendications 1 à 9, caractérisé en ce que les premiers et/ou deuxièmes moyens de liaisons déformables élastiquement comportent des languettes (9, 13, 43) .10. System according to one of claims 1 to 9, characterized in that the first and / or second elastically deformable connecting means comprise tabs (9, 13, 43).
11. Système selon la revendication 10, caractérisé en ce que les languettes sont de formes sensiblement spiralée et uniformément réparties sur une circonférence de la soupape.11. System according to claim 10, characterized in that the tabs are of shapes substantially spirally and uniformly distributed over a circumference of the valve.
12. Système selon l'une des revendications 8 à 11, caractérisé en ce que les moyens de mise en œuvre sont destinés à mettre en œuvre le troisième élément mobile de la soupape.12. System according to one of claims 8 to 11, characterized in that the implementation means are intended to implement the third movable member of the valve.
13. Système selon l'une des revendications 1 à 12, caractérisé en ce que les moyens de mise en œuvre comportent un élément déformable élastiquement monté sur un piston délimitant la chambre à volume variable .13. System according to one of claims 1 to 12, characterized in that the implementation means comprise an elastically deformable element mounted on a piston defining the variable volume chamber.
14. Système selon la revendication 13, caractérisé en ce que l'élément déformable élastique est de type ressort de compression.14. System according to claim 13, characterized in that the elastic deformable element is of the compression spring type.
15. Moteur à gaz sous pression de type (20) caractérisé en ce qu' il comporte au moins une soupape selon l'une des revendications 1 à 14. 15. Type gas engine (20) characterized in that it comprises at least one valve according to one of claims 1 to 14.
PCT/EP2008/061808 2007-09-06 2008-09-05 Low-energy valve system for a pressurized gas engine WO2009030761A1 (en)

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CA2698499A CA2698499A1 (en) 2007-09-06 2008-09-05 Low-energy valve system for a pressurized gas engine
US12/676,573 US20100186720A1 (en) 2007-09-06 2008-09-05 Low-energy valve system for a pressurized gas engine
EP08803777A EP2185845A1 (en) 2007-09-06 2008-09-05 Low-energy valve system for a pressurized gas engine

Applications Claiming Priority (2)

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FR0757397A FR2920854B1 (en) 2007-09-06 2007-09-06 LOW ENERGY VALVE FOR A PRESSURIZED GAS ENGINE
FR0757397 2007-09-06

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EP2185845A1 (en) 2010-05-19
CA2698499A1 (en) 2009-03-12
FR2920854B1 (en) 2012-09-07
US20100186720A1 (en) 2010-07-29
FR2920854A1 (en) 2009-03-13

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